Engine speed governor



y 1938- T. v. HEMMINGSEN 2,116,025

ENGINE SPEED GOVERNOR Filed Oct. 51, 1936 2 Sheets-Sheet l J W W M E May 3, 1938.

T. v. HEMMINGSEN 2,116,025

ENGINE SPEED GOVERNOR Filed Qct. 31, 1956 2 Sheets-Sheet 2 Patented May 3, 1938 PATENT orrics "ENGINE SPEED GOVERNOR ull W 'lorkildvaldemar Hemmingsen, Copenhagen, Denmark appears October 31, 1936, Serial No. 108,676

" In Denmark January 2, 1936 My invention relates to an engine speed governor of thekind comprising a reciprocating governor member, having movably connected to H it-two masses or inertia elementswhich coact with a displaceable passive'lever or a like member Whichis connected with adevice for regulating the "motive fuel supply to the engine, in such amanner that the passive lever at different speeds is displaced in the one or the other direction by the one or the other of the inertia elements. i

The construction of such governors may be performed in different ways. One kind of construction is illustrated on the drawings and its func- 5 tion'will be explained in a moredetailed man: ner in connection with the description of the drawings.

The object of the invention is to provide improvements in connection with governors of the above mentioned kindfthe fact being that the known governors of the kind in question have the deficiency that the inertia elements tend to hamm'er when coacting with the passive lever with the result that the hammering action gives rise 5 todamage. Various means to prevent this have been proposed, e. g. to apply a braking device to the passive lever, so that this leverwhi'ch carries projections or dogs coacting with projections of the inertia elements'of the governor member willremain in the position, to which it has been moved by the governor member. However, the governing mechanism as a whole has a certain degree of elasticity which causes the passive lever to flick back a trifle, sufficient to make the'projections hammer upon each other, if the inertia element, which has displaced the passive lever rea mains in its swung-out position.

The invention has for its object to overcome thesaid deficiency, and is chiefly characterized by a mechanism or means which moves the passive lever or the likemember, after it has been displaced by one of the inertia elements of the governor member, to a "still further position in the direction of the said displacement and main- 45 tains the passive lever in such further position, so thatthe inertia elements when remaining in swung-out position will not be able to hit the passive lever, and hammering consequently is avoided. l

50 According to a further feature of the invention the additional movement of the passive lever beyond the position to which it is-movedby the governor member is suitably effected by means of a cam device. Forinstahce thepassive lever may 55 comprise a cam shaped or curved portion of 1 i Y 7 teams. (01. 264-1) which the mid-part is concentric with the axis, about which the lever is rotatable, but of which the end, parts are curved to a stronger degree than the mid-part, the mechanism further com.- prising a spring-pressed roller adapted to the engine frame and bearing against the middle of the cam, when the passive lever is in its neutral position. Hereby is obtained that the pressure of the spring pressed roller on the lever at the end of the movements imparted to it by the gov- 10 ernor member has a component acting to impart a further motion in the same direction to the passive lever, and to lock and maintain it in such extreme position.

This construction may also be modified in the 15 manner that the passive lever carries the spring pressed roller, whilst the co-acting cam is stationary.

Suitable stops, stop. screws or the like may be arranged to limit the displacement of the passive g lever.

The invention is illustrated in the accompanying drawings.

Fig. 1 is an elevation of a constructional form of such parts of a governor according to the invention, as are necessary to enable the invention to be understood.

Fig. 2 is a partial sectional plan view of the same.

Fig. 3shows another constructional form in a 30 like manner as Fig. 1.

Fig. 4 is a partial sectional plan view of the same.

Fig. 5 is a third constructional form in the like manner as Figs. 1 and 3.

Fig. 6 is the same shown in a like manner as Figs. 2 and 4.

Fig. 7 on a greater scale the inertia elements in one relative position and the passive lever, which is shown in dotted lines in its lower extreme position. i 'Fig. 8 is the same with the inertia elements in another relative position and with the passive lever in the same extreme position, but going to be moved upwardly, and

Fig. 9 is the same with the passive lever in its upper extreme position and with the inertia elements in a third relative position.

Similar parts in each figure are given the same reference numerals.

Referring'now to Figs. 1 and 2, 2 is a pivot pin on the end of a shaft mounted in a fixed bearing 3 and on the pin 2 the passive lever 20 is mounted, At its free end (to the right in the drawing) the passive lever 20 carries projections or dogs 25 and 25 coacting with corresponding projections or dogs on the inertia elements of a governor member not shown in Figs. 1 and 2, but

indicated by H in Figs. '7, 8 and 9, which show also the inertia elements 9 and i5 mounted on pivots it! and H5 respectively on the governor member H and provided with projections l2 and I7 respectively to engage the projections 25 and 26 respectively of the passive lever 20. The inertia members 9 and i5 are influenced by biasing springs 52 with spring guides 53 and 54 as schematically shown, the guides 53 being movable while the guides 5d are stationary but pivotably mounted. The tension of the springs may be adjustable by means of adjusting screws (not shown).

In order to facilitate the understanding it is assumed as example that the tensions of the springs 52 are so adjusted that the inertia element I5 will swing out, when the number of revolutions per minute exceeds say 115, while the inertia element 9 will swing out, when the number of revolutions per minute falls below 120, (i. e. the inertia element 9 returns to its passive position when the number of revolutions exceeds 120). The normal number of revolutions is assumed to be 110.

Now Fig. 7 corresponds to normal running of the engine (or lower speeds), the inertia member |5 being in retracted position, while the inertia member 9 is swung out and consequently will secure that the passive lever remains in its lower extreme position, as any other position of the lever will involve that the projection i2 engages the projection so as to carry the lever 20 down to the said position, when the governor member descends. If, however, the number of revolutions increases to 115 the inertia member l5 will swing out as shown in Fig. 8 so that the projection l1 will engage the projection 25 on the passive lever 23 and move the latter upwardly, thereby involving that the fuel supply is cut off.

rovided that the number of revolutions is only slightly above 115 the passive lever will again be moved down with the governor member I! owing to the inertia element 3 being still swung out so as to engage the projection 25. Consequently the fuel pumps are inactive only for a very short period. This adjustment is. preferred in case of short periods of increased speed, and the governor will soon again adjust the fuel pumps to normal running, the passive lever 20 being moved up and down a few times until the inertia element Hi again returns to its passive position. If, however, the speed increases so much that it reaches or exceeds 120 the inertia element 9 will be retracted, so that the passive lever 20 remains in its upper position (which is the case shown in Fig. 9), whereby the fuel pumps are made inactive until the speed descends again below 120. The inertia element 9 then swings out again and engages with its projection i2 the projection 25 of the passive lever 26 which is therebyreturned to its lower position. If the number of revolutions has not fallen below 115 the lever 20 is moved up and down several times, the inertia element l5 being not retracted until the number of revolutions falls below 115.

As it will be seen the inertia element 9 is in its swung out position during normal running, so that it might hammer with its projection |2 upon the projection 25 of the passive lever 20, if no care was taken to secure that the passive lever was moved a distance beyond the position to which it is moved by the inertia element itself.

From Fig. 7 it appears that a space is provided between the projections l2 and 25, so that hammering is avoided, and the same applies to Fig. 9 as regards the projections l1 and 26.

At its end opposite to the projections 25 and 28 the lever 20 has an extension 21 (Figs. 1 and 2) connected by a joint 28, 29 to the movable guide 30 of a coil spring 3|, the other guide 32 of which is pivotally connected to a stationary bracket 33. The lever 20 or its extension 21 also carries a pivot or the like (not shown) for transferring the governing motion, e. g. to a fuel pump to adjust the supply of fuel. To limit the motion of the lever 20 a pin 50 is provided on the said lever to coact with set screws 5| adjustable in the bearing 3.

. The abovedescribed device acts as follows:

When one or'the other of the projections l2 and I! on the inertia members of the governor member II has moved the lever 20 to one side of the other (i. e. to the displaced positions indicated by dotted lines A and B in Fig. l), the pressure of the spring 3| moves the lever 23 somewhat beyond the position to which it has been moved by the coaction of the projection |2 with 25 or of I! with 26, so that the projections in question are moved apart from each other as indicated in Figs. 7 and 9, and thus the said projections are prevented from hammering upon each other during the subsequent movements of the inertia members.

In the constructional form shown in Figs. 3 and 4 the same reference numerals are used as in Figs. 1 and 2, but here the extension 21 carries a cam-shaped element 34 coacting with a roller 35 mounted in a slide block 36 acted on by a spring 3|. The block 36 is slidably mounted in a stationary guide 31, and the other end of the spring acts on a stationary guide 38 adjustable by means of an adjustable screw 39 screwed into a plate 40 connected to the guide 31 by bolts 4|. The central part of the cam 34 forms a circular are having its centre in the axis of the pivot pin 2, while the outer portions of the cam 34 form curves lying inside the said circular arc, e. g. along its chords. The extension 27 also carries a pin 22 for transferring the governing motion to a fuel pump or similar. adjusting device.

When the lever 20 is displaced so that the roller 35 no longer acts on the circular portion of the cam 34, the roller exerts, by means of the spring 3 I, a pressure on the lever 20 having a component which acts to impart to the said lever an additional motion in the same direction as the direction in which it has been moved, so that the lever 20 is moved beyond the position to which it was moved by the governor member H.

In the constructional form according to Figs. 5 and 6 the lever 20 carries the roller 35 influenced by the spring 3|, the roller 35 being mounted on a pivot 42 carried by a chain link 43 with which the spring 3| coacts. The roller 35 is thus pressed against the stationary cam 34 which in this case forms part of the bearing 3. The cam 34 has a shape similar to the cam 34 according to Figs. 3 and 4, and the device acts in a similar way, the lever 20 being caused by the roller 35 acting on the outer portion of the cam 34 to receive an additional motion at the end of its displacement.

As in Figs. 1 and 2, the lever 20 in Figs. 3 and 4 is fitted with a pin and the bracket 3 with set-screws 5|, while in Figs. 5 and 6 a somewhat modified arrangement of pin 50 on lever 20 and set-screws 5| on the bracket 3 is shown for adjustably limiting the displacement of the lever 20.

I claim:

1. In an engine speed governor of the kind described, a reciprocating governor member, two spring-biased inertia elements movably connected to said governor member, a displaceable passive lever adapted to coact with said inertia elements, said lever being displaced in one direction by one of the inertia elements and in the other direction by the other of the inertia elements when the speed exceeds or falls below certain values, said lever being connected with a device for regulating the motive fuel supply to the engine, a mechanism'adapted to move the passive lever after it has been displaced by one of the inertia members of the governor member to a still further position in the direction of the displacement and to maintain the passive lever in such further position.

2. An engine speed governor according to claim 1 in which the mechanism for effecting the additional movement of the passive lever beyond the position to which it is moved by the inertia element of the governor member comprises a cam device. 7

3. An engine speed governor according to claim 1 in which the passive lever comprises an arcuate cam, the mid-portion of which is concentric with the axis of rotation of the lever, the end parts of which are curved to a greater degree than the mid-part, the mechanism further comprising a spring-pressedroller adapted to the engine frame and bearing against the middle of the cam, when the passive lever is in its neutral position.

4. An engine speed governor according to claim 1 in which the passive lever is provided with a spring influenced roller, a stationary cam coacting with said roller, said cam having a mid-part concentric with the axis of rotation of the lever and end parts curved to a greater degree than the mid-part, the spring-pressed roller bearing against the middle of the cam, when the passive lever is in its neutral position.

TORKILD VALDEMAR HEMMINGSEN. 

